WO2020025343A1 - Variable spacing flange pulley for variable-speed drive - Google Patents
Variable spacing flange pulley for variable-speed drive Download PDFInfo
- Publication number
- WO2020025343A1 WO2020025343A1 PCT/EP2019/069396 EP2019069396W WO2020025343A1 WO 2020025343 A1 WO2020025343 A1 WO 2020025343A1 EP 2019069396 W EP2019069396 W EP 2019069396W WO 2020025343 A1 WO2020025343 A1 WO 2020025343A1
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- WIPO (PCT)
- Prior art keywords
- shaft
- relative
- flange
- pulley
- peripheral wall
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H9/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members
- F16H9/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion
- F16H9/04—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes
- F16H9/12—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members
- F16H9/125—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members characterised by means for controlling the geometrical interrelationship of pulleys and the endless flexible member, e.g. belt alignment or position of the resulting axial pulley force in the plane perpendicular to the pulley axis
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/32—Friction members
- F16H55/52—Pulleys or friction discs of adjustable construction
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
- F16H63/04—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism
- F16H63/06—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism the final output mechanism having an indefinite number of positions
- F16H63/067—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism the final output mechanism having an indefinite number of positions mechanical actuating means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
- F16H63/30—Constructional features of the final output mechanisms
- F16H63/34—Locking or disabling mechanisms
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H9/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members
- F16H9/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion
- F16H9/04—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes
- F16H9/12—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members
- F16H9/14—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members using only one pulley built-up out of adjustable conical parts
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H9/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members
- F16H9/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion
- F16H9/04—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes
- F16H9/12—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members
- F16H9/16—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members using two pulleys, both built-up out of adjustable conical parts
- F16H9/18—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members using two pulleys, both built-up out of adjustable conical parts only one flange of each pulley being adjustable
Definitions
- the present invention relates to a variable spacing flange pulley for a variable speed drive.
- the field of the present invention is that of continuously variable transmission systems (also known with the English acronym CVT for Continuous Variable Transmission).
- CVT Continuous Variable Transmission
- Such a system takes place between a driving shaft and a driven shaft and makes it possible to continuously adapt the speed ratio (of rotation) between the driven shaft and the driving shaft.
- a belt mounted between a driving pulley and a driven pulley is used.
- Each pulley has two flanges and for at least one of the pulleys the spacing between the two flanges is variable. Most often, the two pulleys have a variable spacing of their flanges.
- the spacing between the flanges of a pulley most often varies either according to the load (torque) to be transmitted, or according to the speed of rotation.
- Such a system allows electronic management of the transmission ratio under all operating conditions.
- the electronics can be programmed to provide on demand either a high-performance vehicle or with optimized consumption.
- the present invention therefore aims to provide an essentially mechanical solution allowing at least two different modes of management of the transmission ratio.
- the present invention provides a pulley having:
- a first flange called the fixed flange mounted immobile longitudinally with respect to the shaft
- a mechanical control mechanism for longitudinal displacement of the second flange relative to the shaft comprising:
- locking means in at least one position are provided between the first set and the second set.
- the operating mode of the pulley in a transmission system can be modified: there is the “normal” operating mode in which the locking is inactive and in which the first assembly and the second assembly rotate relatively to one another. the other as a function of the pulley load and an “adapted” operating mode when the locking system blocks the relative position of the first assembly with respect to the second assembly.
- the locking means comprise for example, on the one hand, a finger extending radially and, on the other hand, a hole formed in a peripheral wall, the finger being movable between a position in which it is entirely inside the peripheral wall and a position in which it projects into the hole in the peripheral wall.
- the finger extending radially, it is subjected to centrifugal force and comes out of its housing if its speed of rotation is high enough.
- the locking means comprise a locking finger, this can also extend (and move) longitudinally relative to the shaft.
- the finger can then, for example, lock between them two substantially transverse walls.
- Such a finger can also be associated with an unlocking mechanism.
- a locking between the first set and the second set is preferably carried out when the second set is substantially in a position corresponding to one end of said angular range.
- this end will correspond to a maximum load transmitted by the pulley.
- Mechanical stops most often define the angular range in which the second set can move relative to the first set.
- the pulley may further comprise at least two movable catches articulated around an axis arranged in a plane transverse to the shaft and whose angular position around its axis is given by the angular position of the second together with respect to the shaft, and a counterweight is guided each time in abutment, on the one hand, on a movable latch and, on the other hand, on the face of the movable flange opposite to the fixed flange.
- the first assembly can for example have:
- a first cylindrical part mounted on the shaft and comprising on its outer face, opposite the shaft, at least one helical groove,
- the second set can then present:
- a plate said plate being arranged such that the bottom, the peripheral wall and the plate form a housing for receiving the torsion spring at least one in number,
- said pulley further comprising an intermediate assembly with: • a second cylindrical part mounted at least partially around the first cylindrical part and comprising a finger engaged in the helical groove, said second cylindrical part being slidably mounted in translation parallel to the shaft.
- each movable latch has an axis of articulation relative to the plate and is guided radially in translation relative to the second cylindrical part.
- the first set can have:
- each movable latch has, on the one hand, an axis of articulation relative to the plate and, on the other hand, an arm s 'extending in a helical groove made in the peripheral wall of the second set.
- the present invention further relates to a belt variable speed drive comprising two pulleys mounted on parallel shafts, characterized in that one of the pulleys is a pulley as described above.
- FIG. 1A is a schematic view of a continuous belt transmission in a first transmission ratio
- FIG. 1B corresponds to FIG. 1A for another transmission ratio
- FIG. 2 is an exploded view of a pulley intended for a transmission of the type of that illustrated in FIG. 1,
- FIG. 3 is a perspective view in section of the pulley of FIG. 2 assembled
- FIG. 4A is a sectional view along the section line IV-IV of FIG. 3,
- FIG. 4B is a detailed view of FIG. 4A
- FIG. 5A is a sectional view corresponding to FIG. 4A but in a different position
- FIG. 5B is a detailed view of FIG. 5A
- FIGS. 6A to 6D are views in longitudinal section of the pulley of FIGS. 2 to 5 in various operating modes (load, speed),
- FIG. 7 shows in perspective and in section a pulley which can be used in cooperation with the pulley of FIGS. 2 to 6 to form a continuous transmission
- FIG. 9 shows in perspective and in section a pulley according to the invention in an alternative embodiment with respect to Figures 2 to 6, and
- FIGS 1 A and 1 B each show a continuously variable transmission system (also known with the acronym CVT for Continuous Variable Transmission). Such a system takes place between a driving shaft 2 and a driven shaft 4 and makes it possible to continuously adapt the speed ratio (of rotation) between the driven shaft 4 and the driving shaft 2.
- the driving shaft 2 carries a driving pulley 6 while the driven shaft 4 carries a driven pulley 8.
- the two pulleys are connected together by a belt 10.
- Each pulley has two conical flanges and for at least one of the pulleys the spacing between the two flanges is variable.
- the two pulleys have a variable spacing of their flanges.
- the spacing of the flanges of the driving pulley and / or of the driven pulley is continuously modified so that the radius of curvature of the belt 10 exchange.
- FIG. 1A illustrates a small transmission ratio: the driven shaft 4 rotates slower than the driving shaft 2.
- FIG. 1 B on the contrary, the driven shaft 4 rotates faster than the driving shaft 2.
- FIGS. 2 to 6 illustrate an embodiment of a driving pulley intended for a continuously variable transmission of the type of that illustrated in FIG. 1.
- the pulley illustrated in Figure 2 includes in particular (non-exhaustive list) an outer flange 12, an inner flange 14, weights 16 cooperating with Iinguets 18 and the inner flange 14, a central ring 20, a plate 22, springs 24 , a socket 26 and a casing 28.
- the outer flange 12 is a conical flange. Its external face visible in FIG. 2 has fins which are optional and which depend on the environment in which said flange comes to take place. These fins provide ventilation in the space in which is placed the transmission to which this pulley belongs.
- the inner face of the outer flange 12 is substantially symmetrical to the inner face visible in FIG. 2 of the inner flange 14.
- the outer flange 12 is mounted on a free end of the sleeve 26 while the inner flange 14 is mounted on the central ring 20.
- the outer flange 12 is stationary longitudinally relative to the 'shaft on which it is mounted (and free to rotate relative thereto) while the inner flange 14 can move longitudinally and can have, as will be seen later, a helical movement relative to the shaft.
- the sleeve 26 has a cylindrical part intended to receive the driving shaft 2.
- the internal face of this sleeve 26 has at one end grooves 30 ( Figures 3 and 6 in particular) to allow its drive by the driving shaft 2 which has corresponding grooves (not shown in the drawing).
- the outer face of the sleeve 26 has at its end provided with the grooves 30 a shoulder 32 used for positioning the outer flange 12 on the sleeve 26.
- the outer face of the sleeve 26 also has a helical groove 34. The latter comes to cooperate with a pin 36 screwed into the central ring 20 so as to guide the movement of the central ring 20 relative to the sleeve 26.
- the pin 36 is screwed radially from the outside through the central ring 20 so that its end penetrates inside the helical groove 34.
- the ends of the latter define mechanical stops limiting the relative movement between the central ring 20 and the bush 26.
- the sleeve 26 also has, on the side opposite the end carrying the outer flange 12, a flange 38 for fixing the casing 28.
- the casing 28 has a bottom 40 of annular shape which is fixed using screws 42 on the periphery of the fixing flange 38.
- the housing 28 further comprises a peripheral wall 44 of generally circular cylindrical shape centered on the sleeve 26 when the housing 28 is fixed to said sleeve 26.
- This peripheral wall 44 extends from the outer edge of the bottom 40 like a skirt in direction of the flanges (inner flange 14 and outer flange 12). It has three bores 46 for fixing a wedge 50 with screws 48.
- the springs 24 are housed in the casing 28. These are torsion springs which are mounted between, on the one hand, the assembly formed by the bush 26 and the casing 28 (these two elements form an integral unit by the 'intermediate screws 42) and, on the other hand, the plate 22.
- the springs 24 are thus housed in a space defined by the casing 28, the sleeve 26 and the plate 22.
- the wedge 50 maintains the plate 22 in the longitudinal position along the driving shaft (or of the sleeve 26 rotated by the driving shaft and not moving longitudinally relative to the latter ).
- the plate 22 however is movable in rotation relative to the sleeve 26. In fact, depending on the stiffness of the springs 24 and the torque transmitted by the driving shaft, the angular position of the plate 22 varies relative to the casing 28 (or socket 26, which is equivalent).
- the plate 22 extends radially with respect to the driving shaft. On the side of the casing 28, it has elements for centering and catching the spring 24 which comes to rest against it.
- the plate 22 has a circular cylindrical hub 52 centered on the bushing 26.
- This hub 52 has, inside, longitudinal grooves 54 receiving ribs 56 extending radially from the central ring 20.
- the plate 22 On the side of the inner flange 14, the plate 22 also has pivot bearings 58, guide slots 60 and a radial housing 62.
- the pivot bearings 58 are intended to receive a pivot axis 64 of a latch 18. They are oriented tangentially. The pivot axes of each latch are thus in a transverse plane relative to the shaft of the pulley.
- the guide slots 60 each receive a guide finger 66 produced in the face of the inner flange 14 facing the plate 22.
- the central ring 20 further comprises on its outer face guide forks 68.
- Each fork has two teeth which each extend radially and which are aligned longitudinally with respect to one another.
- These guide forks 68 each receive (there are three of them in the embodiment illustrated here) a bearing 70 produced at the end of a latch 18.
- the radial housing 62 receives a locking finger 72 prestressed by a return spring 74 towards the interior of the radial housing 62.
- This locking finger 72 is intended to face the peripheral wall 44 of the housing 28. It is movable between a fully retracted position in its radial housing 62, or at least sufficiently retracted so as not to come into contact with the peripheral wall 44, and an extended position in which it projects into an oblong hole 76 extending transversely in the peripheral wall 44.
- the length of the oblong hole 76 corresponds for example between two and three times the diameter of the locking finger 72.
- the pulley mounted is clearly visible in particular in Figures 3 and 6.
- the bush 26 is mounted on the drive shaft so as to be integral with it. It is secured in rotation by the grooves 30 and is blocked in translation by the mounting of the outer flange 12 which is mounted locked in translation against the shoulder 32 using a nut 78 (or the like: see FIG. 6) .
- the sleeve 26 and the casing 28 are mounted so as to be integral with one another.
- the plate 22 by means of the springs 24 takes an angular position relative to the bush 26 (and therefore to the driving shaft) which depends on the torque transmitted by the driving shaft. This plate 22 does not move longitudinally.
- the plate 22 When the plate 22 changes its angular position, it rotates with it the central ring 20 (presence of the ribs 56 cooperating with the longitudinal grooves 54). Due to the connection between the central ring 20 and the pin 36, the central ring 20 then moves in translation relative to the plate 22.
- the latches 18 are pivotally mounted on the pivot bearings 58 of the plate 22 and are guided by the guide forks 68 of the central ring 20.
- the plate 22 changes angular position relative to the sleeve 26 and the central ring 20 has a longitudinal translational movement relative to the plate 22.
- This translational movement carries with it one end of each of the latches 18, said end being able to move radially.
- these lugs 18 being pivotally mounted relative to the plate 22, they change inclination relative to a radial axis.
- the inclination of the lugs 18 changes as a function of the load at the level of the shaft ( or of the transmitted torque).
- the counterweights 16 are each guided between the inner flange 14 and the plate 22 in a known manner so as to be able to move radially between, on the one hand, a substantially conical face of the inner flange 14 and a latch 18 which here forms a ramp along from which the corresponding counterweight 16 moves.
- FIGS. 6A to 6D illustrate four positions of the inner flange 14.
- FIGS. 6A and 6B correspond to a high speed of the vehicle (the speed of the vehicle is proportional to the speed of rotation of the driven shaft and it comes to influence via of the belt behavior at the driving shaft) while FIGS. 6B and 6C correspond to a moderate engine speed.
- FIGS. 6A and 6C correspond to a moderate load on the driving shaft (for example during a cruising speed at moderate speed) while FIGS. 6B and 6D correspond to a high load (acceleration, climb,. ..)
- the counterweights 16 are closer to the driving shaft (or bush 26) than at high rotation speed (speed).
- the load in turn influences the inclination of the lugs 18.
- the latch 18 extends radially, which corresponds to a low load, while in the two other figures, the latch is inclined, towards the flange. interior 14.
- the pulley being a driving pulley, the transmission ratio is therefore lower for the same engine speed at high load.
- This management is carried out using the locking finger 72 and the oblong hole 76.
- the latter is disposed at the peripheral wall 44 of the casing 28 so as to be facing the locking finger 72 when the engine is running high and high load (maximum).
- the locking finger 72 due to the centrifugal force, comes out of its radial housing 62 and penetrates at least partially into the oblong hole 76.
- the locking finger 72 prevents the rotation of the plate in opposite direction and the latches 18 are held in the position corresponding to a high load on the motor.
- Figures 4A and 4B illustrates the locking finger 72 in its retracted position in its radial housing 62. The transmission is then in the so-called economic management mode.
- FIGS. 5A and 5B show the locking finger 72 in its extended or locking position. The transmission is then in the so-called efficient management mode.
- the transition from economic to efficient mode occurs automatically when the speed is high and the load is maximum (or almost maximum). Under the effect of centrifugal force, the locking finger 72 comes out.
- the spring 74 is calibrated to allow the release of the locking finger 72 and the locking in efficient mode from a predetermined engine speed.
- a solenoid 80 is provided with a movable pin positioned opposite the oblong hole 76 so as to be able to act on the locking finger 72 in the direction of the return spring 74, it that is to say to make it return to its radial housing 62.
- the solenoid 80 acts on the locking finger 72 in order to push it back into its radial housing 62.
- the transmission returns to the position illustrated in figure 4.
- the transition to economy mode occurs as soon as full charge at high speed is achieved. It is in fact expected that the locking finger 72 is no longer stuck before returning it to its radial housing.
- the locking finger may be arranged in such and such a manner depending, on the one hand, on the space available at the pulley and, on the other hand, space around the pulley to position the unlocking device.
- Figures 7 and 8 illustrate a driven pulley that can be associated with the driving pulley described above to achieve continuous transmission.
- a pulley driven with an outer flange 1 12 fixed and an inner flange 114 mobile.
- the two flanges, the outer flange 11 and the inner flange 114 are mounted on a sleeve 120 surrounding the driven shaft.
- the outer flange 1 12 is mounted to be integral with the driven shaft.
- the inner flange 114 is movably mounted between the outer flange 1 12 fixed and a set of latches 1 18 forming a part whose shape recalls that of an umbrella. These catches 118 have a predetermined inclination relative to the driven shaft. Between the set of latches 1 18 and the inner flange 114, weights 1 16 are guided to move radially when the speed of rotation of the driven shaft varies. When the speed (of rotation of the driven shaft or that of the vehicle) increases, the internal flange 1 14 approaches the external flange 1 12. When this speed decreases, the belt passing around the pulley tends to move the inner flange 114 away from the outer flange 112.
- Figures 9 and 10 illustrate an alternative embodiment of a driving pulley. This embodiment also makes it possible to vary the transmission ratio according to the load and the speed of rotation of the engine but with a slightly different architecture.
- the pulley is mounted directly on the drive shaft, or driving shaft 2.
- Springs 224 are mounted between the driving shaft 2 and a casing 228 having a peripheral wall 244.
- the angular position of the peripheral wall 244 varies compared to that of the leading tree.
- a plate 222 mounted on a socket 226 driven by the driving shaft 2 here carries Iinguets 218.
- This plate 222 is made integral with the driving shaft 2.
- the latches 218 are pivotally mounted around a tangential axis on the plate 222
- Each latch 218 has a lever which is oriented towards the peripheral wall 244 and the end of which engages in a helical slot 234 produced in the peripheral wall 244.
- the peripheral wall 244 changes its angular position relative to the 'driving shaft 2, and therefore also relative to the plate 222, then the lever pivots the corresponding latch 218 relative to its tangential axis. This produces a variable inclination of the latches 218 as a function of the load applied to the motor shaft (driving shaft 2).
- latches 218 serve as a support surface for the weights 216 which are also supported on a conical face of an inner flange 214 in order to vary its position relative to an outer flange 212.
- the locking in the efficient mode can be done by mounting a locking finger radially on the plate 222 so as to make it cooperate with the peripheral wall 244.
- the operation of the locking finger can be the same as that described above with reference in particular to FIGS. 4 and 5.
- a pulley in which a part whose angular position relative to the shaft of the pulley is variable depending on the torque transmitted to the pulley as well as a locking system which keeps this moving part in a given position. It is preferably a driving pulley of a continuous belt transmission system.
- the present invention is not limited to the embodiments described above by way of nonlimiting examples and to the variants mentioned, but it also relates to all the variant embodiments within the reach of the skilled person.
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Abstract
The aim of the present invention is a pulley having: - a shaft (2); - a first flange (12), called fixed flange, mounted so as to be translationally immovable relative to the shaft; - a second flange (14), called movable flange, mounted so as to be rotated by the shaft but being able to move longitudinally relative thereto; - a mechanism for mechanically controlling the longitudinal movement of the second flange relative to the shaft comprising: - a first assembly (26, 38) mounted on the shaft and rotated thereby; - a second assembly (22) mounted on the shaft by means of at least one torsion spring (24) so that the relative angular position of the second assembly relative to the shaft depends on the torque transferred by the shaft; - means (72) for locking in at least one position between the first assembly and the second assembly.
Description
Poulie à flasque à écartement variable pour variateur de vitesse Variable gauge flange pulley for variable speed drive
La présente invention concerne une poulie à flasque à écartement variable pour variateur de vitesse. The present invention relates to a variable spacing flange pulley for a variable speed drive.
Le domaine de la présente invention est celui des systèmes de transmission à variation continue (connus aussi avec le sigle anglais CVT pour Continuous Variable Transmission). Un tel système vient prendre place entre un arbre menant et un arbre mené et permet d’adapter de manière continue le rapport de vitesse (de rotation) entre l’arbre mené et l’arbre menant. The field of the present invention is that of continuously variable transmission systems (also known with the English acronym CVT for Continuous Variable Transmission). Such a system takes place between a driving shaft and a driven shaft and makes it possible to continuously adapt the speed ratio (of rotation) between the driven shaft and the driving shaft.
Pour faire varier de manière continue le rapport de vitesse (dans une plage prédéterminée), on utilise une courroie montée entre une poulie menante et une poulie menée. Chaque poulie présente deux flasques et pour au moins l’une des poulies l’écartement entre les deux flasques est variable. Le plus souvent, les deux poulies présentent un écartement variable de leurs flasques. To continuously vary the speed ratio (within a predetermined range), a belt mounted between a driving pulley and a driven pulley is used. Each pulley has two flanges and for at least one of the pulleys the spacing between the two flanges is variable. Most often, the two pulleys have a variable spacing of their flanges.
L’écartement entre les flasques d’une poulie varie le plus souvent soit en fonction de la charge (couple) à transmettre, soit en fonction de la vitesse de rotation. On peut par exemple avoir une transmission avec une poulie présentant un écartement de flasque variable en fonction de la vitesse de rotation et l’autre poulie ayant un écartement de flasque variable en fonction du couple transmis. The spacing between the flanges of a pulley most often varies either according to the load (torque) to be transmitted, or according to the speed of rotation. One can for example have a transmission with a pulley having a variable flange spacing as a function of the speed of rotation and the other pulley having a variable flange spacing as a function of the transmitted torque.
On trouve de tels systèmes de transmission notamment sur des véhicules à moteur à deux roues (scooters et autres cyclomoteurs) et sur certains véhicules tels des motoneiges par exemple (non limitatif). There are such transmission systems in particular on two-wheel motor vehicles (scooters and other mopeds) and on certain vehicles such as snowmobiles for example (not limiting).
Avec des systèmes de transmission purement mécaniques, il est possible d’agir sur la manière dont la variation de rapport entre arbre menant et arbre mené se fait en ajustant des masses et/ou des raideurs de ressorts et/ou des dimensions de pièces (pour agir sur un couple par exemple). De cette manière, le comportement du véhicule peut être adapté. Il est par exemple possible d’avoir un véhicule qui réagit promptement lors d’une accélération ou bien par exemple de privilégier pour le véhicule une consommation de carburant peu élevée. Un compromis, le plus souvent entre performances et consommation de carburant, doit alors être trouvé. With purely mechanical transmission systems, it is possible to act on the way in which the variation of ratio between driving shaft and driven shaft is done by adjusting masses and / or stiffnesses of springs and / or dimensions of parts (for act on a couple for example). In this way, the behavior of the vehicle can be adapted. It is for example possible to have a vehicle which reacts quickly during an acceleration or for example to favor for the vehicle a low fuel consumption. A compromise, most often between performance and fuel consumption, must then be found.
Pour optimiser le fonctionnement d’un véhicule muni d’une transmission avec un système de transmission à variation continue (ou en abrégé « transmission continue ») il est ainsi proposé de maîtriser l’écartement entre les flasques d’au moins une poulie. To optimize the operation of a vehicle fitted with a transmission with a continuously variable transmission system (or abbreviated to “continuous transmission”), it is thus proposed to control the spacing between the flanges of at least one pulley.
Il est ainsi par exemple connu sur un scooter de faire varier l’écartement des flasques de la poulie menée en fonction de la vitesse de sortie de la transmission à l’aide d’un système à masselottes tandis que l’écartement des flasques de la poulie menante est géré par un système motorisé. Pour la poulie menante, un moteur électrique géré par une électronique de commande vient déplacer (par l’intermédiaire d’une transmission à
engrenages et/ou vis sans fin) un flasque de la poulie, l’autre restant fixe longitudinalement par rapport à l’arbre moteur. It is thus for example known on a scooter to vary the spacing of the flanges of the driven pulley as a function of the output speed of the transmission using a flyweight system while the spacing of the flanges of the driving pulley is managed by a motorized system. For the driving pulley, an electric motor managed by electronic control comes to move (via a transmission to gears and / or worm) one flange of the pulley, the other remaining fixed longitudinally relative to the motor shaft.
Un tel système permet une gestion électronique du rapport de transmission dans toutes les conditions de fonctionnement. L’électronique peut être programmée pour fournir à la demande soit un véhicule performant, soit avec une consommation optimisée. Such a system allows electronic management of the transmission ratio under all operating conditions. The electronics can be programmed to provide on demand either a high-performance vehicle or with optimized consumption.
Toutefois, cette solution présente l’inconvénient, d'une part, d’être d’un prix de revient élevé et, d'autre part, de présenter un encombrement relativement important car le moteur électrique mis en oeuvre doit être un moteur relativement puissant. However, this solution has the drawback, on the one hand, of being of a high cost price and, on the other hand, of presenting a relatively large bulk since the electric motor used must be a relatively powerful motor. .
La présente invention a alors pour but de fournir une solution essentiellement mécanique permettant au moins deux modes différents de gestion du rapport de transmission. The present invention therefore aims to provide an essentially mechanical solution allowing at least two different modes of management of the transmission ratio.
Avantageusement, il sera possible de pouvoir passer d’un mode de gestion à un autre à la demande de l’utilisateur. Advantageously, it will be possible to be able to switch from one management mode to another at the request of the user.
À cet effet, la présente invention propose une poulie présentant : To this end, the present invention provides a pulley having:
• un arbre, • a tree,
• un premier flasque dit flasque fixe, monté de manière immobile longitudinalement par rapport à l’arbre, A first flange called the fixed flange, mounted immobile longitudinally with respect to the shaft,
• un second flasque dit flasque mobile, monté de manière à être entraîné en rotation par l’arbre mais pouvant se déplacer longitudinalement par rapport à celui-ci, • a second flange, said movable flange, mounted so as to be driven in rotation by the shaft but able to move longitudinally relative to the latter,
• un mécanisme de commande mécanique de déplacement longitudinal du second flasque par rapport à l’arbre comportant : • a mechanical control mechanism for longitudinal displacement of the second flange relative to the shaft comprising:
- un premier ensemble monté sur l’arbre et entraîné en rotation par celui-ci, - a first assembly mounted on the shaft and rotated by it,
- un second ensemble monté sur l’arbre par l’intermédiaire d’au moins un ressort de torsion de telle sorte que la position angulaire relative du second ensemble par rapport à l’arbre dépend du couple transmis par l’arbre. - a second assembly mounted on the shaft by means of at least one torsion spring so that the relative angular position of the second assembly relative to the shaft depends on the torque transmitted by the shaft.
Selon la présente invention, des moyens de verrouillage dans au moins une position sont prévus entre le premier ensemble et le second ensemble. According to the present invention, locking means in at least one position are provided between the first set and the second set.
Il est ainsi possible de maintenir la poulie dans une certaine position. Ainsi, le mode de fonctionnement de la poulie dans un système de transmission peut être modifié : il y a le mode de fonctionnement « normal » dans lequel le verrouillage est inactif et dans lequel le premier ensemble et le second ensemble tournent relativement l’un à l’autre en fonction de la charge de la poulie et un mode de fonctionnement « adapté » lorsque le système de verrouillage vient bloquer la position relative du premier ensemble par rapport au second ensemble. It is thus possible to maintain the pulley in a certain position. Thus, the operating mode of the pulley in a transmission system can be modified: there is the “normal” operating mode in which the locking is inactive and in which the first assembly and the second assembly rotate relatively to one another. the other as a function of the pulley load and an “adapted” operating mode when the locking system blocks the relative position of the first assembly with respect to the second assembly.
Dans une telle poulie, les moyens de verrouillage comportent par exemple, d'une part, un doigt s’étendant radialement et, d'autre part, un trou ménagé dans une
paroi périphérique, le doigt étant mobile entre une position dans laquelle il se trouve entièrement à l’intérieur de la paroi périphérique et une position dans laquelle il vient en saillie dans le trou ménagé dans la paroi périphérique. Le doigt s’étendant radialement, il est soumis à la force centrifuge et vient sortir de son logement si sa vitesse de rotation est assez élevée. Dans cette forme de réalisation, on peut prévoir que la poulie comporte en outre des moyens de déverrouillage avec un pion commandé (par exemple à l’aide d’un électro-aimant ou autre actionneur à deux positions) permettant de repousser le doigt à l’intérieur de la paroi périphérique. In such a pulley, the locking means comprise for example, on the one hand, a finger extending radially and, on the other hand, a hole formed in a peripheral wall, the finger being movable between a position in which it is entirely inside the peripheral wall and a position in which it projects into the hole in the peripheral wall. The finger extending radially, it is subjected to centrifugal force and comes out of its housing if its speed of rotation is high enough. In this embodiment, provision can be made for the pulley to further include unlocking means with a controlled pin (for example using an electromagnet or other two-position actuator) making it possible to push the finger back to the inside the peripheral wall.
Si les moyens de verrouillage comportent un doigt de verrouillage, celui-ci peut aussi s’étendre (et se déplacer) longitudinalement par rapport à l’arbre. Le doigt peut alors par exemple venir verrouiller entre elles deux parois sensiblement transversales. Un tel doigt peut aussi être associé à un mécanisme de déverrouillage. If the locking means comprise a locking finger, this can also extend (and move) longitudinally relative to the shaft. The finger can then, for example, lock between them two substantially transverse walls. Such a finger can also be associated with an unlocking mechanism.
Dans une telle poulie, lorsque le mouvement de rotation relatif du second ensemble par rapport à l’arbre est compris dans une plage angulaire prédéterminée, un verrouillage entre le premier ensemble et le second ensemble est de préférence réalisé lorsque le second ensemble est sensiblement dans une position correspondant à une extrémité de ladite plage angulaire. De préférence, cette extrémité correspondra à une charge maximale transmise par la poulie. Des butées mécaniques définissent le plus souvent la plage angulaire dans laquelle le second ensemble peut se déplacer par rapport au premier ensemble. In such a pulley, when the relative rotational movement of the second set with respect to the shaft is within a predetermined angular range, a locking between the first set and the second set is preferably carried out when the second set is substantially in a position corresponding to one end of said angular range. Preferably, this end will correspond to a maximum load transmitted by the pulley. Mechanical stops most often define the angular range in which the second set can move relative to the first set.
Selon une variante de réalisation préférée, la poulie peut comporter en outre au moins deux linguets mobiles articulés autour d’un axe disposé dans un plan transversal à l’arbre et dont la position angulaire autour de son axe est donnée par la position angulaire du second ensemble par rapport à l’arbre, et une masselotte est guidée à chaque fois en appui, d'une part, sur un linguet mobile et, d'autre part, sur la face du flasque mobile opposée au flasque fixe. According to a preferred embodiment, the pulley may further comprise at least two movable catches articulated around an axis arranged in a plane transverse to the shaft and whose angular position around its axis is given by the angular position of the second together with respect to the shaft, and a counterweight is guided each time in abutment, on the one hand, on a movable latch and, on the other hand, on the face of the movable flange opposite to the fixed flange.
Dans une poulie selon la présente invention, le premier ensemble peut par exemple présenter : In a pulley according to the present invention, the first assembly can for example have:
• une première partie cylindrique montée sur l’arbre et comportant sur sa face extérieure, opposée à l’arbre, au moins une rainure hélicoïdale, A first cylindrical part mounted on the shaft and comprising on its outer face, opposite the shaft, at least one helical groove,
• un fond, et • a background, and
• une paroi périphérique extérieure, • an outer peripheral wall,
le second ensemble pouvant quant à lui alors présenter : the second set can then present:
• un plateau, ledit plateau étant agencé de telle sorte que le fond, la paroi périphérique et le plateau forment un logement pour recevoir le ressort de torsion au nombre d’au moins un, A plate, said plate being arranged such that the bottom, the peripheral wall and the plate form a housing for receiving the torsion spring at least one in number,
et ladite poulie comportant en outre un ensemble intermédiaire avec :
• une seconde partie cylindrique montée au moins partiellement autour de la première partie cylindrique et comportant un doigt en prise dans la rainure hélicoïdale, ladite seconde partie cylindrique étant montée coulissante en translation parallèlement à l’arbre. and said pulley further comprising an intermediate assembly with: • a second cylindrical part mounted at least partially around the first cylindrical part and comprising a finger engaged in the helical groove, said second cylindrical part being slidably mounted in translation parallel to the shaft.
Dans cette forme de réalisation avec en outre des linguets mobiles comme mentionné plus haut, on peut prévoir que chaque linguet mobile présente un axe d’articulation par rapport au plateau et est guidée radialement en translation par rapport à la seconde partie cylindrique. In this embodiment with in addition movable lugs as mentioned above, it can be provided that each movable latch has an axis of articulation relative to the plate and is guided radially in translation relative to the second cylindrical part.
Selon une autre forme de réalisation, le premier ensemble peut présenter : According to another embodiment, the first set can have:
• une première partie cylindrique montée sur l’arbre et • a first cylindrical part mounted on the shaft and
• un plateau monté sur la partie cylindrique, • a plate mounted on the cylindrical part,
et le second ensemble peut présenter : and the second set can present:
• une paroi périphérique relié par le ressort de torsion au nombre d’au moins un directement ou indirectement à l’arbre, ladite paroi périphérique venant recouvrir le plateau du premier ensemble. • a peripheral wall connected by at least one torsion spring directly or indirectly to the shaft, said peripheral wall covering the plate of the first assembly.
Dans cette autre forme de réalisation avec en outre des linguets mobiles comme mentionné plus haut, on peut prévoir que chaque linguet mobile présente, d'une part, un axe d’articulation par rapport au plateau et, d'autre part, un bras s’étendant dans une rainure hélicoïdale réalisée dans la paroi périphérique du second ensemble. In this other embodiment with in addition movable lugs as mentioned above, it can be provided that each movable latch has, on the one hand, an axis of articulation relative to the plate and, on the other hand, an arm s 'extending in a helical groove made in the peripheral wall of the second set.
La présente invention concerne en outre un variateur de vitesse à courroie comportant deux poulies montées sur des arbres parallèles, caractérisé en ce que l’une des poulies est une poulie telle que décrite ci-dessus. The present invention further relates to a belt variable speed drive comprising two pulleys mounted on parallel shafts, characterized in that one of the pulleys is a pulley as described above.
- La figure 1A est une vue schématique d’une transmission continue à courroie dans un premier rapport de transmission, - Figure 1A is a schematic view of a continuous belt transmission in a first transmission ratio,
- La figure 1 B correspond à la figure 1A pour un autre rapport de transmission, FIG. 1B corresponds to FIG. 1A for another transmission ratio,
- La figure 2 est une vue éclatée d’une poulie destinée à une transmission du type de celle illustrée sur la figure 1 , FIG. 2 is an exploded view of a pulley intended for a transmission of the type of that illustrated in FIG. 1,
- La figure 3 est une vue en perspective et en coupe de la poulie de la figure 2 assemblée, FIG. 3 is a perspective view in section of the pulley of FIG. 2 assembled,
- La figure 4A est une vue en coupe selon la ligne de coupe IV-IV de la figure 3, FIG. 4A is a sectional view along the section line IV-IV of FIG. 3,
- La figure 4B est une vue de détail de la figure 4A, FIG. 4B is a detailed view of FIG. 4A,
- La figure 5A est une vue en coupe correspondant à la figure 4A mais dans une position différente, FIG. 5A is a sectional view corresponding to FIG. 4A but in a different position,
- La figure 5B est une vue de détail de la figure 5A,
- Les figures 6A à 6D sont des vues en coupe longitudinale de la poulie des figures 2 à 5 dans divers modes de fonctionnement (charge, régime),FIG. 5B is a detailed view of FIG. 5A, FIGS. 6A to 6D are views in longitudinal section of the pulley of FIGS. 2 to 5 in various operating modes (load, speed),
- La figure 7 montre en perspective et en coupe une poulie pouvant être utilisée en coopération avec la poulie des figures 2 à 6 pour former une transmission continue, FIG. 7 shows in perspective and in section a pulley which can be used in cooperation with the pulley of FIGS. 2 to 6 to form a continuous transmission,
- La figure 8 montre la poulie de la figure 7 en perspective éclatée, - Figure 8 shows the pulley of Figure 7 in exploded perspective,
- La figure 9 montre en perspective et en coupe une poulie selon l’invention dans une variante de réalisation par rapport aux figures 2 à 6, et - Figure 9 shows in perspective and in section a pulley according to the invention in an alternative embodiment with respect to Figures 2 to 6, and
- La figure 10 montre en perspective éclatée la poulie de la figure 9. - Figure 10 shows in exploded perspective the pulley of Figure 9.
Les figures 1 A et 1 B montrent chacune un système de transmission à variation continue (connus aussi avec le sigle anglais CVT pour Continuous Variable Transmission). Un tel système vient prendre place entre un arbre menant 2 et un arbre mené 4 et permet d’adapter de manière continue le rapport de vitesse (de rotation) entre l’arbre mené 4 et l’arbre menant 2. L’arbre menant 2 porte une poulie menante 6 tandis que l’arbre mené 4 porte une poulie menée 8. Les deux poulies sont reliées entre elles par une courroie 10. Figures 1 A and 1 B each show a continuously variable transmission system (also known with the acronym CVT for Continuous Variable Transmission). Such a system takes place between a driving shaft 2 and a driven shaft 4 and makes it possible to continuously adapt the speed ratio (of rotation) between the driven shaft 4 and the driving shaft 2. The driving shaft 2 carries a driving pulley 6 while the driven shaft 4 carries a driven pulley 8. The two pulleys are connected together by a belt 10.
Chaque poulie présente deux flasques coniques et pour au moins l’une des poulies l’écartement entre les deux flasques est variable. Dans la forme de réalisation illustrée ici, les deux poulies présentent un écartement variable de leurs flasques. Pour faire varier de manière continue le rapport de vitesse (dans une plage prédéterminée), l’écartement des flasques de la poulie menante et/ou de la poulie menée est modifié de manière continue de telle sorte que le rayon de courbure de la courroie 10 change. Each pulley has two conical flanges and for at least one of the pulleys the spacing between the two flanges is variable. In the embodiment illustrated here, the two pulleys have a variable spacing of their flanges. To continuously vary the speed ratio (within a predetermined range), the spacing of the flanges of the driving pulley and / or of the driven pulley is continuously modified so that the radius of curvature of the belt 10 exchange.
La figure 1A illustre un petit rapport de transmission : l’arbre mené 4 tourne moins vite que l’arbre menant 2. Sur la figure 1 B, au contraire, l’arbre mené 4 tourne plus vite que l’arbre menant 2. FIG. 1A illustrates a small transmission ratio: the driven shaft 4 rotates slower than the driving shaft 2. In FIG. 1 B, on the contrary, the driven shaft 4 rotates faster than the driving shaft 2.
Les figures 2 à 6 illustrent une forme de réalisation d’une poulie menante destinée à une transmission à variation continue du type de celle illustrée sur la figure 1. FIGS. 2 to 6 illustrate an embodiment of a driving pulley intended for a continuously variable transmission of the type of that illustrated in FIG. 1.
La poulie illustrée sur la figure 2 comporte notamment (liste non exhaustive) un flasque extérieur 12, un flasque intérieur 14, des masselottes 16 coopérant avec des Iinguets 18 et le flasque intérieur 14, une bague centrale 20, un plateau 22, des ressorts 24, une douille 26 et un carter 28. The pulley illustrated in Figure 2 includes in particular (non-exhaustive list) an outer flange 12, an inner flange 14, weights 16 cooperating with Iinguets 18 and the inner flange 14, a central ring 20, a plate 22, springs 24 , a socket 26 and a casing 28.
Le flasque extérieur 12 est un flasque conique. Sa face extérieure visible sur la figure 2 présente des ailettes qui sont optionnelles et qui dépendent de l’environnement dans lequel ledit flasque vient prendre place. Ces ailettes permettent d’assurer une ventilation dans l’espace dans lequel est placée la transmission à laquelle cette poulie appartient. La face intérieure du flasque extérieur 12 est sensiblement symétrique à la face intérieure visible sur la figure 2 du flasque intérieur 14. Pour chacun
des deux flasques, c’est-à-dire le flasque extérieur 12 et le flasque intérieur 14, on trouve à chaque fois une partie centrale qui de manière classique est utilisée, d'une part, pour le montage direct ou indirect sur l’arbre menant (non illustré sur les figures 2-6) et, d'autre part, pour déterminer l’espace minimum entre le flasque extérieur 12 et le flasque intérieur 14 (et éventuellement aussi l’espace maximum). The outer flange 12 is a conical flange. Its external face visible in FIG. 2 has fins which are optional and which depend on the environment in which said flange comes to take place. These fins provide ventilation in the space in which is placed the transmission to which this pulley belongs. The inner face of the outer flange 12 is substantially symmetrical to the inner face visible in FIG. 2 of the inner flange 14. For each of the two flanges, that is to say the outer flange 12 and the inner flange 14, there is each time a central part which conventionally is used, on the one hand, for direct or indirect mounting on the leading shaft (not illustrated in Figures 2-6) and, secondly, to determine the minimum space between the outer flange 12 and the inner flange 14 (and possibly also the maximum space).
Comme on peut le voir sur la figure 3 notamment, le flasque extérieur 12 est monté sur une extrémité libre de la douille 26 tandis que le flasque intérieur 14 est monté sur la bague centrale 20. Le flasque extérieur 12 est immobile longitudinalement par rapport à l’arbre sur lequel il est monté (et libre en rotation par rapport à celui-ci) tandis que le flasque intérieur 14 peut se déplacer longitudinalement et peut avoir, comme il ressort par la suite, un mouvement hélicoïdal par rapport à l’arbre. As can be seen in Figure 3 in particular, the outer flange 12 is mounted on a free end of the sleeve 26 while the inner flange 14 is mounted on the central ring 20. The outer flange 12 is stationary longitudinally relative to the 'shaft on which it is mounted (and free to rotate relative thereto) while the inner flange 14 can move longitudinally and can have, as will be seen later, a helical movement relative to the shaft.
La douille 26 présente une partie cylindrique destinée à recevoir l’arbre menant 2. La face intérieure de cette douille 26 présente à une extrémité des cannelures 30 (figures 3 et 6 notamment) pour permettre son entrainement par l’arbre menant 2 qui présente des cannelures correspondantes (non illustrées au dessin). The sleeve 26 has a cylindrical part intended to receive the driving shaft 2. The internal face of this sleeve 26 has at one end grooves 30 (Figures 3 and 6 in particular) to allow its drive by the driving shaft 2 which has corresponding grooves (not shown in the drawing).
La face extérieure de la douille 26 présente à son extrémité munie des cannelures 30 un épaulement 32 utilisé pour le positionnement du flasque extérieur 12 sur la douille 26. La face extérieure de la douille 26 présente aussi une rainure hélicoïdale 34. Cette dernière vient coopérer avec un pion 36 vissé dans la bague centrale 20 de manière à guider le mouvement de la bague centrale 20 par rapport à la douille 26. Le pion 36 est vissé radialement par l’extérieur à travers la bague centrale 20 de telle sorte que son extrémité pénètre à l’intérieur de la rainure hélicoïdale 34. Les extrémités de cette dernière définissent des butées mécaniques limitant le mouvement relatif entre la bague centrale 20 et la douille 26. The outer face of the sleeve 26 has at its end provided with the grooves 30 a shoulder 32 used for positioning the outer flange 12 on the sleeve 26. The outer face of the sleeve 26 also has a helical groove 34. The latter comes to cooperate with a pin 36 screwed into the central ring 20 so as to guide the movement of the central ring 20 relative to the sleeve 26. The pin 36 is screwed radially from the outside through the central ring 20 so that its end penetrates inside the helical groove 34. The ends of the latter define mechanical stops limiting the relative movement between the central ring 20 and the bush 26.
La douille 26 présente en outre, du côté opposé à l’extrémité portant le flasque extérieur 12, une bride 38 de fixation pour le carter 28. The sleeve 26 also has, on the side opposite the end carrying the outer flange 12, a flange 38 for fixing the casing 28.
Le carter 28 présente un fond 40 de forme annulaire qui est fixé à l’aide de vis 42 sur le pourtour de la bride 38 de fixation. Le carter 28 comporte en outre une paroi périphérique 44 de forme globalement cylindrique circulaire centrée sur la douille 26 lorsque le carter 28 est fixé à ladite douille 26. Cette paroi périphérique 44 s’étend à partir du bord extérieur du fond 40 comme une jupe en direction des flasques (flasque intérieur 14 et flasque extérieur 12). Elle présente trois alésages 46 pour la fixation par vis 48 d’une cale 50. The casing 28 has a bottom 40 of annular shape which is fixed using screws 42 on the periphery of the fixing flange 38. The housing 28 further comprises a peripheral wall 44 of generally circular cylindrical shape centered on the sleeve 26 when the housing 28 is fixed to said sleeve 26. This peripheral wall 44 extends from the outer edge of the bottom 40 like a skirt in direction of the flanges (inner flange 14 and outer flange 12). It has three bores 46 for fixing a wedge 50 with screws 48.
Les ressorts 24 sont logés dans le carter 28. Il s’agit de ressorts de torsion qui sont montés entre, d'une part, l’ensemble formé par la douille 26 et le carter 28 (ces deux éléments forment un ensemble solidaire par l’intermédiaire des vis 42) et, d'autre part, le plateau 22. Les ressorts 24 sont ainsi logés dans un espace délimité par le carter 28, la
douille 26 et le plateau 22. La cale 50 maintient le plateau 22 en position longitudinale le long de l’arbre menant (ou de la douille 26 entraîné en rotation par l’arbre menant et ne se déplaçant pas longitudinalement par rapport à celui-ci). The springs 24 are housed in the casing 28. These are torsion springs which are mounted between, on the one hand, the assembly formed by the bush 26 and the casing 28 (these two elements form an integral unit by the 'intermediate screws 42) and, on the other hand, the plate 22. The springs 24 are thus housed in a space defined by the casing 28, the sleeve 26 and the plate 22. The wedge 50 maintains the plate 22 in the longitudinal position along the driving shaft (or of the sleeve 26 rotated by the driving shaft and not moving longitudinally relative to the latter ).
Le plateau 22 toutefois est mobile en rotation par rapport à la douille 26. En effet, en fonction de la raideur des ressorts 24 et du couple transmis par l’arbre menant, la position angulaire du plateau 22 varie par rapport au carter 28 (ou douille 26, ce qui est équivalent). The plate 22 however is movable in rotation relative to the sleeve 26. In fact, depending on the stiffness of the springs 24 and the torque transmitted by the driving shaft, the angular position of the plate 22 varies relative to the casing 28 (or socket 26, which is equivalent).
Le plateau 22 s’étend radialement par rapport à l’arbre menant. Du côté du carter 28, il présente des éléments pour le centrage et l’accroche du ressort 24 qui vient reposer contre lui. The plate 22 extends radially with respect to the driving shaft. On the side of the casing 28, it has elements for centering and catching the spring 24 which comes to rest against it.
En son centre, le plateau 22 présente un moyeu 52 cylindrique circulaire centré sur la douille 26. Ce moyeu 52 comporte à l’intérieur des rainures longitudinales 54 recevant des nervures 56 s’étendant radialement à partir de la bague centrale 20. Ainsi, la bague centrale 20 et le plateau 22 se déplacent l’un par rapport à l’autre selon un mouvement de translation longitudinale tandis que le plateau 22 tourne autour de la douille 26 (rotation pure) et que la bague centrale 20 se déplace hélicoïdalement par rapport à la douille 26. At its center, the plate 22 has a circular cylindrical hub 52 centered on the bushing 26. This hub 52 has, inside, longitudinal grooves 54 receiving ribs 56 extending radially from the central ring 20. Thus, the central ring 20 and the plate 22 move relative to each other in a longitudinal translational movement while the plate 22 rotates around the sleeve 26 (pure rotation) and that the central ring 20 moves helically relative to at socket 26.
Du côté du flasque intérieur 14, le plateau 22 présente en outre des paliers de pivotement 58, des fentes de guidage 60 et un logement radial 62. On the side of the inner flange 14, the plate 22 also has pivot bearings 58, guide slots 60 and a radial housing 62.
Les paliers de pivotement 58, ici au nombre de trois, sont destinés à recevoir un axe de pivotement 64 d’un linguet 18. Ils sont orientés tangentiellement. Les axes de pivotement de chaque linguet se trouvent ainsi dans un plan transversal par rapport à l’arbre de la poulie. The pivot bearings 58, here three in number, are intended to receive a pivot axis 64 of a latch 18. They are oriented tangentially. The pivot axes of each latch are thus in a transverse plane relative to the shaft of the pulley.
Les fentes de guidage 60 reçoivent quant à elles chacune un doigt de guidage 66 réalisé dans la face du flasque intérieur 14 faisant face au plateau 22. The guide slots 60 each receive a guide finger 66 produced in the face of the inner flange 14 facing the plate 22.
Outre les éléments déjà décrits, la bague centrale 20 comporte en outre sur sa face extérieure des fourches de guidage 68. Chaque fourche présente deux dents qui s’étendent chacune radialement et qui sont alignées longitudinalement l’une par rapport à l’autre. Ces fourches de guidage 68 reçoivent chacune (elles sont au nombre de trois dans l’exemple de réalisation illustré ici) un palier 70 réalisé au niveau d’une extrémité d’un linguet 18. In addition to the elements already described, the central ring 20 further comprises on its outer face guide forks 68. Each fork has two teeth which each extend radially and which are aligned longitudinally with respect to one another. These guide forks 68 each receive (there are three of them in the embodiment illustrated here) a bearing 70 produced at the end of a latch 18.
Le logement radial 62 reçoit un doigt de verrouillage 72 précontraint par un ressort de rappel 74 vers l’intérieur du logement radial 62. Ce doigt de verrouillage 72 est destiné à faire face à la paroi périphérique 44 du carter 28. Il est mobile entre une position entièrement rentrée dans son logement radial 62, ou tout du moins suffisamment rentré pour ne pas venir au contact de la paroi périphérique 44, et une position sortie dans laquelle il vient en saillie dans un trou oblong 76 s’étendant transversalement dans la
paroi périphérique 44. La longueur du trou oblong 76 correspond par exemple entre deux et trois fois le diamètre du doigt de verrouillage 72. The radial housing 62 receives a locking finger 72 prestressed by a return spring 74 towards the interior of the radial housing 62. This locking finger 72 is intended to face the peripheral wall 44 of the housing 28. It is movable between a fully retracted position in its radial housing 62, or at least sufficiently retracted so as not to come into contact with the peripheral wall 44, and an extended position in which it projects into an oblong hole 76 extending transversely in the peripheral wall 44. The length of the oblong hole 76 corresponds for example between two and three times the diameter of the locking finger 72.
La poulie montée est bien visible notamment sur les figures 3 et 6. La douille 26 est montée sur l’arbre menant de manière à être solidaire avec celui-ci. Elle est solidaire en rotation par les cannelures 30 et est bloquée en translation par le montage du flasque extérieur 12 qui est monté bloqué en translation contre l’épaulement 32 à l’aide d’un écrou 78 (ou similaire : cf. figure 6). The pulley mounted is clearly visible in particular in Figures 3 and 6. The bush 26 is mounted on the drive shaft so as to be integral with it. It is secured in rotation by the grooves 30 and is blocked in translation by the mounting of the outer flange 12 which is mounted locked in translation against the shoulder 32 using a nut 78 (or the like: see FIG. 6) .
Comme expliqué plus haut, la douille 26 et le carter 28 sont montés de manière à être solidaire l’un de l’autre. Le plateau 22 par l’intermédiaire des ressorts 24 prend une position angulaire par rapport à la douille 26 (et donc à l’arbre menant) qui dépend du couple transmis par l’arbre menant. Ce plateau 22 ne se déplace pas longitudinalement. As explained above, the sleeve 26 and the casing 28 are mounted so as to be integral with one another. The plate 22 by means of the springs 24 takes an angular position relative to the bush 26 (and therefore to the driving shaft) which depends on the torque transmitted by the driving shaft. This plate 22 does not move longitudinally.
Lorsque le plateau 22 change de position angulaire, il entraîne en rotation avec lui la bague centrale 20 (présence des nervures 56 coopérant avec les rainures longitudinales 54). Du fait de la liaison entre la bague centrale 20 et le pion 36, la bague centrale 20 se déplace alors en translation par rapport au plateau 22. When the plate 22 changes its angular position, it rotates with it the central ring 20 (presence of the ribs 56 cooperating with the longitudinal grooves 54). Due to the connection between the central ring 20 and the pin 36, the central ring 20 then moves in translation relative to the plate 22.
Les linguets 18 sont montés en pivotement sur les paliers de pivotement 58 du plateau 22 et sont guidés par les fourches de guidage 68 de la bague centrale 20. Ainsi, lorsque le couple exercé sur l’arbre varie, le plateau 22 change de position angulaire par rapport à la douille 26 et la bague centrale 20 a un mouvement de translation longitudinal relatif par rapport au plateau 22. Ce mouvement de translation entraîne avec lui une extrémité de chacun des linguets 18, ladite extrémité pouvant se déplacer radialement. En outre, ces linguets 18 étant montés pivotants par rapport au plateau 22, ils changent d’inclinaison par rapport à un axe radial. Ainsi donc, de même que la position angulaire du plateau 22 par rapport à la douille 26 et de même que la position longitudinale de la bague centrale 20, l’inclinaison des linguets 18 change en fonction de la charge au niveau de l’arbre (ou du couple transmis). The latches 18 are pivotally mounted on the pivot bearings 58 of the plate 22 and are guided by the guide forks 68 of the central ring 20. Thus, when the torque exerted on the shaft varies, the plate 22 changes angular position relative to the sleeve 26 and the central ring 20 has a longitudinal translational movement relative to the plate 22. This translational movement carries with it one end of each of the latches 18, said end being able to move radially. In addition, these lugs 18 being pivotally mounted relative to the plate 22, they change inclination relative to a radial axis. Thus, as well as the angular position of the plate 22 relative to the bush 26 and like the longitudinal position of the central ring 20, the inclination of the lugs 18 changes as a function of the load at the level of the shaft ( or of the transmitted torque).
Les masselottes 16 sont chacune guidées entre le flasque intérieur 14 et le plateau 22 de manière connue afin de pouvoir se déplacer radialement entre, d'une part, une face sensiblement conique du flasque intérieur 14 et un linguet 18 qui forme ici une rampe le long de laquelle se déplace la masselotte 16 correspondante. The counterweights 16 are each guided between the inner flange 14 and the plate 22 in a known manner so as to be able to move radially between, on the one hand, a substantially conical face of the inner flange 14 and a latch 18 which here forms a ramp along from which the corresponding counterweight 16 moves.
Les masselottes 16 qui sont soumises à la force centrifuge lorsque l’arbre menant tourne vont ainsi s’éloigner de l’arbre menant lorsque la vitesse de rotation augmente tendant ainsi à rapprocher le flasque intérieur 14 du flasque extérieur 12. En fonction de la charge au niveau de l’arbre menant, ce mouvement sera influencé par l’inclinaison des linguets 18.
Les figures 6A à 6D illustrent quatre positions du flasque intérieur 14. Les figures 6A et 6B correspondent à une vitesse élevée du véhicule (la vitesse du véhicule est proportionnelle à la vitesse de rotation de l’arbre mené et elle vient influencer par l’intermédiaire de la courroie le comportement au niveau de l’arbre menant) tandis que les figures 6B et 6C correspondent à un régime moteur modéré. The counterweights 16 which are subjected to centrifugal force when the driving shaft rotates will thus move away from the driving shaft when the speed of rotation increases, thus tending to bring the inner flange 14 closer to the outer flange 12. Depending on the load at the level of the driving shaft, this movement will be influenced by the inclination of the latches 18. FIGS. 6A to 6D illustrate four positions of the inner flange 14. FIGS. 6A and 6B correspond to a high speed of the vehicle (the speed of the vehicle is proportional to the speed of rotation of the driven shaft and it comes to influence via of the belt behavior at the driving shaft) while FIGS. 6B and 6C correspond to a moderate engine speed.
En outre, les figures 6A et 6C correspondent à une charge modérée sur l’arbre menant (par exemple lors d’un régime de croisière à vitesse modérée) tandis que les figures 6B et 6D correspondent à une charge élevée (accélération, montée, ...) In addition, FIGS. 6A and 6C correspond to a moderate load on the driving shaft (for example during a cruising speed at moderate speed) while FIGS. 6B and 6D correspond to a high load (acceleration, climb,. ..)
On remarque qu’à vitesse de rotation modérée, les masselottes 16 sont plus proches de l’arbre menant (ou douille 26) qu’à vitesse de rotation (régime) élevée. Note that at moderate rotation speed, the counterweights 16 are closer to the driving shaft (or bush 26) than at high rotation speed (speed).
La charge quant à elle influence l’inclinaison des linguets 18. Sur les figures 6A et 6B, le linguet 18 s’étend radialement ce qui correspond à une charge faible tandis que sur les deux autres figures, le linguet est inclinée, vers le flasque intérieur 14. Pour les faibles régimes moteur, on constate qu’à charge élevée le flasque intérieur 14 est plus éloigné du flasque extérieur 12 qu’à charge modérée. La poulie étant une poulie menante, le rapport de transmission est donc moins élevé pour un même régime moteur à charge élevée. The load in turn influences the inclination of the lugs 18. In FIGS. 6A and 6B, the latch 18 extends radially, which corresponds to a low load, while in the two other figures, the latch is inclined, towards the flange. interior 14. For low engine speeds, it can be seen that at high load the internal flange 14 is more distant from the external flange 12 than at moderate load. The pulley being a driving pulley, the transmission ratio is therefore lower for the same engine speed at high load.
Il est proposé ici de pouvoir choisir mécaniquement un mode de gestion économique ou un mode de gestion favorisant les performances (optimisation de la puissance) pour la transmission continue. It is proposed here to be able to mechanically choose an economic management mode or a management mode promoting performance (power optimization) for continuous transmission.
Cette gestion est réalisée à l’aide du doigt de verrouillage 72 et du trou oblong 76. Ce dernier est disposé au niveau de la paroi périphérique 44 du carter 28 de manière à se trouver face au doigt de verrouillage 72 lorsque le moteur est à régime élevé et à charge élevée (maximale). Dans cette situation, le doigt de verrouillage 72, du fait de la force centrifuge, sort de son logement radial 62 et pénètre au moins partiellement dans le trou oblong 76. Lorsque la charge diminue, le doigt de verrouillage 72 empêche la rotation du plateau en sens inverse et les linguets 18 sont maintenus dans la position correspondant à une charge élevée du moteur. This management is carried out using the locking finger 72 and the oblong hole 76. The latter is disposed at the peripheral wall 44 of the casing 28 so as to be facing the locking finger 72 when the engine is running high and high load (maximum). In this situation, the locking finger 72, due to the centrifugal force, comes out of its radial housing 62 and penetrates at least partially into the oblong hole 76. When the load decreases, the locking finger 72 prevents the rotation of the plate in opposite direction and the latches 18 are held in the position corresponding to a high load on the motor.
Les figures 4A et 4B illustre le doigt de verrouillage 72 dans sa position rentrée dans son logement radial 62. La transmission est alors dans le mode de gestion dit économique. Figures 4A and 4B illustrates the locking finger 72 in its retracted position in its radial housing 62. The transmission is then in the so-called economic management mode.
Les figures 5A et 5B montrent le doigt de verrouillage 72 dans sa position sortie, ou de verrouillage. La transmission est alors dans le mode de gestion dit performant. FIGS. 5A and 5B show the locking finger 72 in its extended or locking position. The transmission is then in the so-called efficient management mode.
Le passage du mode économique au mode performant se fait automatiquement lorsque le régime est élevé et que la charge est maximale (ou quasi maximale). Sous l’effet de la force centrifuge, le doigt de verrouillage 72 sort. Le ressort
de rappel 74 est taré pour permettre la sortie du doigt de verrouillage 72 et le verrouillage en mode performant à partir d’un régime moteur prédéterminé. The transition from economic to efficient mode occurs automatically when the speed is high and the load is maximum (or almost maximum). Under the effect of centrifugal force, the locking finger 72 comes out. The spring 74 is calibrated to allow the release of the locking finger 72 and the locking in efficient mode from a predetermined engine speed.
Pour le passage en mode économique à partir du mode performant, il est prévu un solénoïde 80 avec un pion mobile positionné face au trou oblong 76 de manière à pouvoir agir sur le doigt de verrouillage 72 dans le sens du ressort de rappel 74, c’est-à- dire pour le faire rentrer dans son logement radial 62. For the transition to economic mode from the efficient mode, a solenoid 80 is provided with a movable pin positioned opposite the oblong hole 76 so as to be able to act on the locking finger 72 in the direction of the return spring 74, it that is to say to make it return to its radial housing 62.
Si le mode économique est commandé lorsque le moteur est à pleine charge et haut régime, alors le solénoïde 80 agit sur le doigt de verrouillage 72 afin de le repousser dans son logement radial 62. Lorsque la charge diminue, la transmission revient dans la position illustrée sur la figure 4. If the economy mode is controlled when the engine is at full load and high speed, then the solenoid 80 acts on the locking finger 72 in order to push it back into its radial housing 62. When the load decreases, the transmission returns to the position illustrated in figure 4.
Si le mode économique est commandé alors que la transmission est verrouillée en mode performant, le passage en mode économique se fait dès que la pleine charge à haut régime est réalisée. On attend en effet que le doigt de verrouillage 72 ne soit plus coincé pour venir le rentrer dans son logement radial. If the economy mode is controlled while the transmission is locked in efficient mode, the transition to economy mode occurs as soon as full charge at high speed is achieved. It is in fact expected that the locking finger 72 is no longer stuck before returning it to its radial housing.
En variante de réalisation, on pourrait avoir un doigt de verrouillage se déplaçant longitudinalement. En effet, le verrouillage pourrait être réalisé entre deux faces s’étendant globalement transversalement par rapport à l’arbre. On pourrait ainsi avoir un doigt précontraint élastiquement porté par le plateau 22 et venant en appui sur le fond 40 du carter 28. Ce dernier présenterait un trou dans lequel l’extrémité du doigt viendrait se loger. In an alternative embodiment, one could have a locking finger moving longitudinally. Indeed, the locking could be achieved between two faces extending generally transversely with respect to the shaft. It would thus be possible to have a preloaded finger resiliently carried by the plate 22 and coming to bear on the bottom 40 of the casing 28. The latter would have a hole in which the end of the finger would be housed.
Comme il apparaîtra à l’homme du métier, en fonction de l’environnement, le doigt de verrouillage pourra être disposé de telle ou telle manière en fonction, d'une part, de la place dont on dispose au niveau de la poulie et, d'autre part, de la place autour de la poulie pour positionner le dispositif de déverrouillage. As will be apparent to a person skilled in the art, depending on the environment, the locking finger may be arranged in such and such a manner depending, on the one hand, on the space available at the pulley and, on the other hand, space around the pulley to position the unlocking device.
Les figures 7 et 8 illustrent une poulie menée pouvant être associée à la poulie menante décrite ci-dessus pour réaliser une transmission continue. Figures 7 and 8 illustrate a driven pulley that can be associated with the driving pulley described above to achieve continuous transmission.
Il est proposé ici d’avoir une poulie menée avec un flasque extérieur 1 12 fixe et un flasque intérieur 114 mobile. Les deux flasques, le flasque extérieur 1 12 et le flasque intérieur 114 sont montés sur une douille 120 entourant l’arbre mené. Ici aussi, le flasque extérieur 1 12 est monté pour être solidaire de l’arbre mené. It is proposed here to have a pulley driven with an outer flange 1 12 fixed and an inner flange 114 mobile. The two flanges, the outer flange 11 and the inner flange 114 are mounted on a sleeve 120 surrounding the driven shaft. Here too, the outer flange 1 12 is mounted to be integral with the driven shaft.
Le flasque intérieur 114 est monté mobile entre le flasque extérieur 1 12 fixe et un ensemble de linguets 1 18 formant une pièce dont la forme rappelle celle d’un parapluie. Ces linguets 118 présentent une inclinaison prédéterminée par rapport à l’arbre mené. Entre l’ensemble de linguets 1 18 et le flasque intérieur 114, des masselottes 1 16 sont guidées pour se déplacer radialement lorsque la vitesse de rotation de l’arbre mené varie. Lorsque la vitesse (de rotation de l’arbre mené ou celle du véhicule) augmente, le flasque intérieur 1 14 se rapproche du flasque extérieur 1 12. Quand cette vitesse diminue,
la courroie passant autour de la poulie tend à éloigner le flasque intérieur 114 du flasque extérieur 112. The inner flange 114 is movably mounted between the outer flange 1 12 fixed and a set of latches 1 18 forming a part whose shape recalls that of an umbrella. These catches 118 have a predetermined inclination relative to the driven shaft. Between the set of latches 1 18 and the inner flange 114, weights 1 16 are guided to move radially when the speed of rotation of the driven shaft varies. When the speed (of rotation of the driven shaft or that of the vehicle) increases, the internal flange 1 14 approaches the external flange 1 12. When this speed decreases, the belt passing around the pulley tends to move the inner flange 114 away from the outer flange 112.
Les figures 9 et 10 illustrent une variante de réalisation d’une poulie menante. Cette forme de réalisation permet également de faire varier le rapport de transmission en fonction de la charge et de la vitesse de rotation du moteur mais avec une architecture un peu différente. Figures 9 and 10 illustrate an alternative embodiment of a driving pulley. This embodiment also makes it possible to vary the transmission ratio according to the load and the speed of rotation of the engine but with a slightly different architecture.
Les références utilisées pour la description de ce mode de réalisation correspondent aux références utilisées dans la description des figures 2 à 6 mais augmentées de 200 pour désigner des pièces similaires. The references used for the description of this embodiment correspond to the references used in the description of Figures 2 to 6 but increased by 200 to designate similar parts.
Il semble inutile de décrire dans le détail le mode de réalisation des figures 9 et 10. Les différences principales par rapport au mode de réalisation des figures 2 à 6 décrit en détail plus haut seront indiquées ainsi que le mode de fonctionnement de cette variante de réalisation. It seems unnecessary to describe in detail the embodiment of Figures 9 and 10. The main differences from the embodiment of Figures 2 to 6 described in detail above will be indicated as well as the mode of operation of this alternative embodiment .
Le montage de la poulie est réalisé directement sur l’arbre moteur, ou arbre menant 2. Des ressorts 224 sont montés entre l’arbre menant 2 et un carter 228 présentant une paroi périphérique 244. Ainsi la position angulaire de la paroi périphérique 244 varie par rapport à celle de l’arbre menant. The pulley is mounted directly on the drive shaft, or driving shaft 2. Springs 224 are mounted between the driving shaft 2 and a casing 228 having a peripheral wall 244. Thus the angular position of the peripheral wall 244 varies compared to that of the leading tree.
Un plateau 222 monté sur une douille 226 entraîné par l’arbre menant 2 porte ici des Iinguets 218. Ce plateau 222 est rendu solidaire de l’arbre menant 2. Les linguets 218 sont montés pivotants autour d’un axe tangentiel sur le plateau 222. Chaque linguet 218 présente un levier qui s’oriente vers la paroi périphérique 244 et dont l’extrémité vient s’engager dans une fente hélicoïdale 234 réalisée dans la paroi périphérique 244. Quand la paroi périphérique 244 change de position angulaire par rapport à l’arbre menant 2, et donc aussi par rapport au plateau 222, alors le levier vient faire pivoter le linguet 218 correspondante par rapport à son axe tangentiel. On réalise ainsi une inclinaison variable des linguets 218 en fonction de la charge appliquée sur l’arbre moteur (arbre menant 2). A plate 222 mounted on a socket 226 driven by the driving shaft 2 here carries Iinguets 218. This plate 222 is made integral with the driving shaft 2. The latches 218 are pivotally mounted around a tangential axis on the plate 222 Each latch 218 has a lever which is oriented towards the peripheral wall 244 and the end of which engages in a helical slot 234 produced in the peripheral wall 244. When the peripheral wall 244 changes its angular position relative to the 'driving shaft 2, and therefore also relative to the plate 222, then the lever pivots the corresponding latch 218 relative to its tangential axis. This produces a variable inclination of the latches 218 as a function of the load applied to the motor shaft (driving shaft 2).
Ici aussi les linguets 218 servent de surface d’appui à des masselottes 216 qui s’appuient en outre sur une face conique d’un flasque intérieur 214 afin de faire varier sa position par rapport à un flasque extérieur 212. Here also the latches 218 serve as a support surface for the weights 216 which are also supported on a conical face of an inner flange 214 in order to vary its position relative to an outer flange 212.
Dans cette forme de réalisation, le verrouillage dans le mode performant peut se faire en montant un doigt de verrouillage radialement sur le plateau 222 de manière à le faire coopérer avec la paroi périphérique 244. Le fonctionnement du doigt de verrouillage peut être le même que celui décrit plus haut en référence notamment aux figures 4 et 5. In this embodiment, the locking in the efficient mode can be done by mounting a locking finger radially on the plate 222 so as to make it cooperate with the peripheral wall 244. The operation of the locking finger can be the same as that described above with reference in particular to FIGS. 4 and 5.
Dans cette forme de réalisation, on a donc également une poulie dans laquelle une pièce dont la position angulaire par rapport à l’arbre de la poulie est variable
en fonction du couple transmis au niveau de la poulie ainsi qu’un système de verrouillage qui vient maintenir cette pièce mobile dans une position donnée. Il s’agit de préférence d’une poulie menante d’un système de transmission continue à courroie. In this embodiment, there is therefore also a pulley in which a part whose angular position relative to the shaft of the pulley is variable depending on the torque transmitted to the pulley as well as a locking system which keeps this moving part in a given position. It is preferably a driving pulley of a continuous belt transmission system.
Dans la description ci-dessus, il est envisagé un verrouillage dans une position correspondant à une charge élevée (ou maximale). Toutefois, il est envisageable d’avoir un verrouillage dans une autre position, à charge minimale ou bien pour une charge intermédiaire prédéterminée. On peut aussi envisager un verrouillage dans deux positions distinctes sur un même dispositif. In the above description, it is envisaged to lock in a position corresponding to a high (or maximum) load. However, it is possible to have a lock in another position, at minimum load or for a predetermined intermediate load. It is also possible to envisage locking in two distinct positions on the same device.
La présente invention ne se limite pas aux formes de réalisation décrites ci- dessus à titre d’exemples non limitatifs et aux variantes évoquées mais elle concerne également toutes les variantes de réalisation à la portée de l’homme du métier.
The present invention is not limited to the embodiments described above by way of nonlimiting examples and to the variants mentioned, but it also relates to all the variant embodiments within the reach of the skilled person.
Claims
1. Poulie présentant : 1. Pulley presenting:
• un arbre (2), • a tree (2),
• un premier flasque (12 ; 212) dit flasque fixe, monté de manière immobile longitudinalement par rapport à l’arbre, A first flange (12; 212) said to be fixed flange, mounted immobile longitudinally relative to the shaft,
« un second flasque (14 ; 214) dit flasque mobile, monté de manière à être entraîné en rotation par l’arbre mais pouvant se déplacer longitudinalement par rapport à celui-ci, "A second flange (14; 214) said mobile flange, mounted so as to be driven in rotation by the shaft but able to move longitudinally relative to the latter,
• un mécanisme de commande mécanique de déplacement longitudinal du second flasque par rapport à l’arbre comportant : • a mechanical control mechanism for longitudinal displacement of the second flange relative to the shaft comprising:
- un premier ensemble (26, 38 ; 222) monté sur l’arbre et entraîné en rotation par celui-ci, - a first assembly (26, 38; 222) mounted on the shaft and driven in rotation by the latter,
- un second ensemble (22 ; 238) monté sur l’arbre par l’intermédiaire d’au moins un ressort de torsion (24 ; 224) de telle sorte que la position angulaire relative du second ensemble par rapport à l’arbre dépend du couple transmis par l’arbre, - a second assembly (22; 238) mounted on the shaft by means of at least one torsion spring (24; 224) so that the relative angular position of the second assembly relative to the shaft depends on the torque transmitted by the tree,
caractérisée en ce que characterized in that
des moyens de verrouillage (72) dans au moins une position sont prévus entre le premier ensemble et le second ensemble. locking means (72) in at least one position are provided between the first set and the second set.
2. Poulie selon la revendication 1 , caractérisée en ce que les moyens de verrouillage comportent, d'une part, un doigt (72) s’étendant radialement et, d'autre part, un trou (76) ménagé dans une paroi périphérique (44), le doigt (72) étant mobile entre une position dans laquelle il se trouve entièrement à l’intérieur de la paroi périphérique (44) et une position dans laquelle il vient en saillie dans le trou (76) ménagé dans la paroi périphérique (44). 2. Pulley according to claim 1, characterized in that the locking means comprise, on the one hand, a finger (72) extending radially and, on the other hand, a hole (76) formed in a peripheral wall ( 44), the finger (72) being movable between a position in which it is entirely inside the peripheral wall (44) and a position in which it projects into the hole (76) formed in the peripheral wall (44).
3. Poulie selon la revendication 2, caractérisée en ce qu’elle comporte en outre des moyens de déverrouillage (80) avec un pion commandé permettant de repousser le doigt (72) à l’intérieur de la paroi périphérique (44). 3. Pulley according to claim 2, characterized in that it further comprises unlocking means (80) with a controlled pin enabling the finger (72) to be pushed back inside the peripheral wall (44).
4. Poulie selon l'une des revendications 1 à 3, caractérisée en ce que le mouvement de rotation relatif du second ensemble par rapport à l’arbre est compris dans une plage angulaire prédéterminée, et en ce qu’un verrouillage entre le premier ensemble et le second ensemble est réalisé lorsque le second ensemble est sensiblement dans une position correspondant à une extrémité de ladite plage angulaire.
4. Pulley according to one of claims 1 to 3, characterized in that the relative rotational movement of the second set relative to the shaft is within a predetermined angular range, and in that a locking between the first set and the second set is produced when the second set is substantially in a position corresponding to one end of said angular range.
5. Poulie selon l'une des revendications 1 à 4, caractérisée en ce qu’elle comporte en outre au moins deux linguets (18 ; 218) mobiles articulés autour d’un axe disposé dans un plan transversal à l’arbre et dont la position angulaire autour de son axe est donnée par la position angulaire du second ensemble par rapport à l’arbre, et en ce qu’une masselotte (16 ; 216) est guidée à chaque fois en appui, d'une part, sur un linguet (18 ; 218) mobile et, d'autre part, sur la face du flasque (14 ; 214) mobile opposée au flasque (12 ; 212) fixe. 5. Pulley according to one of claims 1 to 4, characterized in that it further comprises at least two movable lugs (18; 218) articulated around an axis arranged in a plane transverse to the shaft and the angular position around its axis is given by the angular position of the second assembly with respect to the shaft, and in that a counterweight (16; 216) is guided each time by bearing, on the one hand, on a latch (18; 218) movable and, on the other hand, on the face of the movable flange (14; 214) opposite the fixed flange (12; 212).
6. Poulie selon l'une des revendications 1 à 5, caractérisée en ce que 6. Pulley according to one of claims 1 to 5, characterized in that
le premier ensemble présente the first set presents
• une première partie cylindrique (26) montée sur l’arbre et comportant sur sa face extérieure, opposée à l’arbre, au moins une rainure hélicoïdale (34), A first cylindrical part (26) mounted on the shaft and comprising on its outer face, opposite the shaft, at least one helical groove (34),
• un fond (38, 40), et • a background (38, 40), and
• une paroi périphérique (44) extérieure, • an outer peripheral wall (44),
en ce que le second ensemble présente in that the second set presents
• un plateau (22), ledit plateau étant agencé de telle sorte que le fond (38, 40), la paroi périphérique (44) et le plateau (22) forment un logement pour recevoir le ressort de torsion (24) au nombre d’au moins un, • a plate (22), said plate being arranged such that the bottom (38, 40), the peripheral wall (44) and the plate (22) form a housing for receiving the torsion spring (24) in number 'at least one,
et en ce que ladite poulie comporte un ensemble intermédiaire avec and in that said pulley comprises an intermediate assembly with
• une seconde partie cylindrique (20) montée au moins partiellement autour de la première partie cylindrique (26) et comportant un doigt (36) en prise dans la rainure hélicoïdale (34), ladite seconde partie cylindrique (20) étant montée coulissante en translation parallèlement à l’arbre. • a second cylindrical part (20) mounted at least partially around the first cylindrical part (26) and comprising a finger (36) engaged in the helical groove (34), said second cylindrical part (20) being slidably mounted in translation parallel to the tree.
7. Poulie selon les revendications 5 et 6, caractérisée en ce que chaque linguet (18) mobile présente un axe d’articulation par rapport au plateau (22) et est guidée radialement en translation par rapport à la seconde partie cylindrique (20). 7. Pulley according to claims 5 and 6, characterized in that each movable latch (18) has an axis of articulation relative to the plate (22) and is guided radially in translation relative to the second cylindrical part (20).
8. Poulie selon l'une des revendications 1 à 5, caractérisée en ce que 8. Pulley according to one of claims 1 to 5, characterized in that
le premier ensemble présente the first set presents
• une première partie cylindrique (226) montée sur l’arbre et • a first cylindrical part (226) mounted on the shaft and
• un plateau (222) monté sur la partie cylindrique (226), • a plate (222) mounted on the cylindrical part (226),
et en ce que le second ensemble présente
• une paroi périphérique (244) relié par le ressort de torsion (224) au nombre d’au moins un directement ou indirectement à l’arbre (2), ladite paroi périphérique (244) venant recouvrir le plateau (222) du premier ensemble. and in that the second set presents • a peripheral wall (244) connected by the torsion spring (224) at least one in number directly or indirectly to the shaft (2), said peripheral wall (244) covering the plate (222) of the first set .
9. Poulie selon les revendications 5 et 8, caractérisée en ce que chaque linguet (218) mobile présente, d'une part, un axe d’articulation par rapport au plateau (222) et, d'autre part, un bras s’étendant dans une rainure hélicoïdale (234) réalisée dans la paroi périphérique (244) du second ensemble. 9. Pulley according to claims 5 and 8, characterized in that each movable latch (218) has, on the one hand, an axis of articulation relative to the plate (222) and, on the other hand, an arm s' extending in a helical groove (234) formed in the peripheral wall (244) of the second set.
10. Variateur de vitesse à courroie comportant deux poulies montées sur des arbres parallèles, caractérisé en ce que l’une des poulies est une poulie selon l'une des revendications 1 à 9.
10. Belt speed variator comprising two pulleys mounted on parallel shafts, characterized in that one of the pulleys is a pulley according to one of claims 1 to 9.
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US17/264,996 US11835133B2 (en) | 2018-08-01 | 2019-07-18 | Variable spacing flange pulley for variable-speed drive |
CN201980050942.1A CN112585382B (en) | 2018-08-01 | 2019-07-18 | Variable-spacing flange pulley for a transmission |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR1857212 | 2018-08-01 | ||
FR1857212A FR3084714B1 (en) | 2018-08-01 | 2018-08-01 | VARIABLE SPACER FLANGE PULLEY FOR SPEED VARIATOR |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2020025343A1 true WO2020025343A1 (en) | 2020-02-06 |
Family
ID=65200980
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2019/069396 WO2020025343A1 (en) | 2018-08-01 | 2019-07-18 | Variable spacing flange pulley for variable-speed drive |
Country Status (4)
Country | Link |
---|---|
US (1) | US11835133B2 (en) |
CN (1) | CN112585382B (en) |
FR (1) | FR3084714B1 (en) |
WO (1) | WO2020025343A1 (en) |
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US11835120B2 (en) * | 2021-11-19 | 2023-12-05 | Team Industries, Inc. | Continuously variable transmission clutch |
CN114001156B (en) * | 2021-11-23 | 2023-08-11 | 重庆宗申集研机电科技有限公司 | Gear shifting mechanism and two-gear automatic gear shifting system |
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Also Published As
Publication number | Publication date |
---|---|
CN112585382B (en) | 2023-04-28 |
US20210324946A1 (en) | 2021-10-21 |
US11835133B2 (en) | 2023-12-05 |
FR3084714B1 (en) | 2020-07-03 |
CN112585382A (en) | 2021-03-30 |
FR3084714A1 (en) | 2020-02-07 |
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